CN104350284B - Turbomachinery - Google Patents
Turbomachinery Download PDFInfo
- Publication number
- CN104350284B CN104350284B CN201380030055.0A CN201380030055A CN104350284B CN 104350284 B CN104350284 B CN 104350284B CN 201380030055 A CN201380030055 A CN 201380030055A CN 104350284 B CN104350284 B CN 104350284B
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- China
- Prior art keywords
- impeller
- axle
- differential screw
- compressor
- thread
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D17/08—Centrifugal pumps
- F04D17/10—Centrifugal pumps for compressing or evacuating
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/053—Shafts
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/053—Shafts
- F04D29/054—Arrangements for joining or assembling shafts
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/266—Rotors specially for elastic fluids mounting compressor rotors on shafts
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The present invention is the turbomachinery (S1 ~ S3) for the axle (2) for possessing the impeller (1a) of rotation and rotary power being transferred to the impeller, possesses differential screw (3), the differential screw (3), which possesses, to be located at a side and threadingly engages in the impeller threaded connection (3a) of the impeller and be located at another side and threadingly engage in the axle thread junction surface (3b) of the axle, the impeller and the axle are fastened, the differential screw (3) is formed as：The diameter of thread for being formed at ridge of the diameter of thread with being formed at the axle thread junction surface of the ridge of the impeller threaded connection is identical, the convolution direction for being formed at the ridge of the impeller threaded connection and the convolution direction for the ridge for being formed at the axle thread junction surface are same direction, moreover, the spacing that the gap ratio for being formed at the ridge of the impeller threaded connection is formed at the ridge at the axle thread junction surface is smaller.
Description
Technical field
The present invention relates to turbomachinery.The application based on June 11st, 2012 Japanese publication Japanese Patent Application 2012-
No. 131785 and CLAIM OF PRIORITY, by its content quotation in this.
Background technology
In the turbomachinery such as turbo-compressor or booster, possesses the impeller by being rotated from axle transmitting rotary power
(patent document 1 to patent document 4).
In patent document 1 and patent document 2, such composition is disclosed：Pass through the positive spiral shell for making to be formed at impeller and axle
Line and negative thread are threadedly engaged and combine centring location, so that impeller and axle be fastened.
In patent document 3, such composition is disclosed：By using tensioning bolt, so as to hardly make impeller relative
It is in rotary moving in axle, just impeller is firmly fastened to axle.
In patent document 4, such composition is disclosed：By using the spacing and the spiral shell of axle side of the threaded portion of impeller side
The different differential screw of the spacing in line portion, so that impeller and axle be fastened.
Citation
Patent document
Patent document 1：Japanese Patent Publication 5-52356 publications
Patent document 2：Japanese Patent Publication 5-57450 publications
Patent document 3：No. 4876867 publications of Japanese Patent No.
Patent document 4：No. 4089802 publications of Japanese Patent No..
The content of the invention
Problems to be solved by the invention
However, in the composition disclosed in patent document 1 and patent document 2, when impeller and axle are fastened, it is necessary to make
Impeller is in rotary moving relative to axle.I.e., it is necessary to make impeller in rotary moving and while insensibly close to axle.Therefore, by impeller
The amount of movement of impeller when being installed on axle much increases than the amount of movement of impeller when making to be installed on axle impeller is in rotary moving.
Therefore, in the technology of patent document 1 and patent document 2, required workload increases when impeller and axle are fastened.
In addition, in order to prevent impeller from deviateing with axle along direction of rotation, expecting there is sufficiently friction between impeller and axle
Power.It is therefore preferred that when installing impeller and axle, after impeller is contacted with seated surface (end face of the axle contacted with impeller),
Further impeller is pressed into along the direction towards axle, impeller elastic deformation is made in advance.But, in patent document 1 and patent document 2
Technology in, after being contacted in impeller with seated surface, frictional force is acted between impeller and seated surface, thus frictional resistance
Increase.That is, in order to by impeller along towards the press-in of the direction of axle, it is necessary to big fastening torque.
In addition, in patent document 3, due to using tensioning bolt, thus separately needing the complicated and big dress such as hydraulic tensioner
Put.In addition, workload (energy) increase of the degree of stretching caused by pretension.
In addition, in patent document 4, by using differential screw so as to eliminate in patent document 1 and patent document 2
Problem etc., but threadingly engage in the diameter of thread of the threaded portion of impeller and threadingly engage in the diameter of thread of the threaded portion of axle not
Together.Accordingly, there exist in order to relax the stress that the different position of the diameter of thread is produced and differential screw length this
New problem.That is, due to being formed with the stage portion with big step difference between the different position of the diameter of thread in this wise, thus should
Stress concentration at stage portion becomes big.Therefore, it is necessary to which stage portion is formed as into long conical by its shape, stress is reduced as far as possible
Concentrate.If however, considered the solution of new problem in this wise and extend the length of differential screw, the use with patent document 3
Similarly, workload increases the degree of the stretching caused by pretension to the situation of tensioning bolt.
The present invention be in view of such situation and make, its object is to there is provided suppress due to pretension work
The turbomachinery of the increase of amount.
The solution used to solve the problem
The 1st mode of the present invention is the turbine for the axle for possessing the impeller of rotation and rotary power being transferred to the impeller
Tool, possesses differential screw, and the differential screw possesses the impeller threaded connection for being located at a side and threadingly engaging in foregoing impeller
Be located at another side and threadingly engage in the axle thread junction surface of aforementioned axis, foregoing impeller and aforementioned axis are fastened.This is differential
Screw shaped turns into：It is formed at the diameter of thread of the ridge of foregoing impeller threaded connection and is formed at aforementioned axis threaded connection
Ridge the diameter of thread it is identical, the convolution direction for being formed at the ridge of foregoing impeller threaded connection is foregoing with being formed at
The convolution direction of the ridge at axle thread junction surface is same direction, moreover, being formed at the screw thread of foregoing impeller threaded connection
The spacing that the gap ratio of tooth is formed at the ridge of aforementioned axis threaded connection is smaller.
In the 2nd mode of the present invention, the turbomachinery in foregoing 1st mode, foregoing impeller threaded connection is than foregoing
Axle thread junction surface is longer.
The 3rd mode of the present invention, in the turbomachinery in foregoing 1st or the 2nd mode, foregoing impeller is along its rotary shaft
Possesses the through hole being threadedly engaged with the foregoing impeller threaded connection of foregoing differential screw, in the remote foregoing of foregoing through hole
The opening portion of axle, releasably provided with by the lid of the opening port blocking.
The 4th mode of the present invention, in the turbomachinery of any one of foregoing 1st ~ 3 mode, foregoing differential screw is by warm
The conductivity material higher than foregoing impeller is formed.
The 5th mode of the present invention, in the turbomachinery of foregoing 4th mode, foregoing impeller is formed by titanium alloy, foregoing difference
Dynamic screw is formed by ferrous materials.
The 6th mode of the present invention, in the foregoing 1st ~ 5 turbomachinery of any one, possesses the foregoing impeller of suppression relative
In the rotation restraint mechanism in rotary moving of aforementioned axis.
The 7th mode of the present invention, in the turbomachinery of foregoing 6th mode, foregoing rotation restraint mechanism is pin member, its
Using the rotation direction of principal axis of foregoing impeller as length direction, be embedded in the deviation rotary shaft for being located at foregoing impeller position it is chimeric
Hole and be located at aforementioned axis deviation rotary shaft position embedded hole.
The 8th mode of the present invention, in the turbomachinery of foregoing 7th mode, multiple foregoing pin members are along with foregoing impeller
Rotary shaft centered on circumferential direction to configure at equal intervals.
The 9th mode of the present invention, in the turbomachinery of foregoing 6th mode, foregoing rotation restraint mechanism possesses：It is chimeric prominent
Rise, deviate from the outer shape of the rotation direction of principal axis viewing of foregoing impeller from round-shaped, also, in foregoing impeller and aforementioned axis
A side along it is foregoing rotation direction of principal axis protrude and set；And embedded hole, the opposing party of foregoing impeller and aforementioned axis is located at, also,
Foregoing mosaic process is fitted together to.
The present invention the 10th mode, in the turbomachinery of foregoing 9th mode, foregoing mosaic process have using rotary shaft as
The shape of center of gravity.
The 11st mode of the present invention, in the turbomachinery of any one of foregoing 1st ~ 10 mode, is formed at aforementioned axis spiral shell
The convolution direction setting of the ridge at line junction surface be due to the counter-force that is produced when aforementioned axis rotates foregoing differential screw with
The direction that the fastening force of aforementioned axis is improved.
The 12nd mode of the present invention, in the turbomachinery of any one of foregoing 1st ~ 11 mode, it is preferable that in foregoing difference
The end face of the foregoing impeller side of dynamic screw, connecting hole or card provided with the holding section for being sticked in the fixture for rotating the differential screw
Projection is closed, being provided with foregoing impeller makes the through hole that foregoing connecting hole or engaging protrusion are exposed.
The 13rd mode of the present invention, in the turbomachinery of foregoing 12nd mode, being sticked in rotates foregoing differential screw
Fixture holding section foregoing connecting hole or engaging protrusion there is shape using the rotary shaft of foregoing impeller as center of gravity.
The effect of invention
In the turbomachinery of the present invention, the screw thread especially using the ridge for making to be formed at impeller threaded connection is straight
The diameter of thread identical differential screw of ridge of the footpath with being formed at axle thread junction surface, impeller and axle are fastened.Therefore, do not have
Be necessary as in the past like that in order to relax extend the length of differential screw in the stress of the different position generation of the diameter of thread.Cause
This, can suppress the increase of the workload due to pretension.
Brief description of the drawings
Fig. 1 is the side cross-sectional, view of the schematic configuration for the turbo-compressor for showing the 1st embodiment involved in the present invention.
Fig. 2 is for illustrating compressor impeller and axle that the turbo-compressor in the 1st embodiment of the present invention possesses
Terminal operation schematic diagram.
Fig. 3 A are the side cross-sectional, views for the schematic configuration for showing the turbo-compressor in the 2nd embodiment of the present invention.
Fig. 3 B are the front views for the schematic configuration for showing the turbo-compressor in the 2nd embodiment of the present invention.
Fig. 4 A are the side cross-sectional, views for the schematic configuration for showing the turbo-compressor in the 3rd embodiment of the present invention.
Fig. 4 B are the front views for the schematic configuration for showing the turbo-compressor in the 3rd embodiment of the present invention.
Fig. 5 is the sectional view for the variation for showing the turbo-compressor in the 1st embodiment of the present invention.
Embodiment
Hereinafter, referring to the drawings, the embodiment to turbomachinery involved in the present invention is described in detail.In addition,
In figures in the following, in order that each part turns into the size that can be recognized, the engineer's scale of each part is suitably changed.
In addition, in the following description, as an example of the turbomachinery of the present invention, illustrating turbo-compressor
Machine, but the turbomachinery of the present invention is not limited to turbo-compressor, can be applied to the turbine that booster etc. possesses impeller and axle
The entirety of machinery.
(the 1st embodiment)
Fig. 1 is the side cross-sectional of the schematic configuration for the turbo-compressor S1 for showing the 1st embodiment involved in the present invention
Figure.Turbo-compressor S1 spues the gas compressions such as air as compressed gas, as shown in figure 1, possess compressor 1, axle 2,
Differential screw 3 and driver element 4.
Compressor 1 is by, by the device of gas compression, being possessed compressor impeller 1a (impeller of the invention) by driving
With compressor housing 1b.
Compressor impeller 1a is the device for assigning kinetic energy to gas and being allowed to acceleration, makes to suck from rotary shaft L directions
The radial impeller that gas accelerates and spued along radial direction.As shown in figure 1, compressor impeller 1a possesses the base for being anchored on axle 2
The bottom 1c and multiple blade 1d being arranged at equal intervals on basal part 1c surface along direction of rotation.
In basal part 1c, embedded hole 1e is formed with, embedded hole 1e is open towards driver element 4, is embedded in axle 2 and is possessed
Mosaic process 2a.In basal part 1c inside, it is formed with as the receiving sky that differential screw 3 is connected and accommodated with embedded hole 1e
Between through hole 1f.In the internal face of the receiving space, being formed with can be threadedly engaged by the part of a side of differential screw 3
Thread groove constitute female threaded portion (not shown).
Specifically, the through hole 1f that end face from the compressor impeller 1a of differential screw 3 front end are exposed is made in substrate
Rotary shaft L-shaped of the portion 1c inside along compressor impeller 1a into.The end of through hole 1f axle 2 (or embedded hole 1e) side into
To accommodate the receiving space of differential screw 3.Therefore, the rotary shaft L of through hole 1f and embedded hole 1e along compressor impeller 1a with
Linearly continuously configure.
In addition, through hole 1f has the internal diameter bigger than the fixture 10 (reference picture 2) described later for rotating differential screw 3,
So that the fixture 10 is inserted into insertion.
In addition, through hole 1f, in the front end face for being opened on compressor impeller 1a, (that is, compressor impeller 1a's is located at and axle 2
The end face of the opposite side of the end face of side) opening portion 1j sides internal face, be formed with for making opening portion 1j occlusions
The female threaded portion (not shown) that nose shell (lid) 9 is screwed.
By it is such constitute the compressor impeller 1a constituted according to the gas compressed by such as titanium alloy, aluminium alloy or
Stainless steel is formed.
Compressor housing 1b is the device for the stream to form the outer shape of compressor 1 and internally have gas, is accommodated
Compressor impeller 1a and configure.
In addition, compressor housing 1b possesses：Suction opening 1g, gas is sucked；Diffuser 1h, will pass through compressor impeller
1a and the gas that accelerates slow down and compressed；Scroll stream 1i, the stream as compressed gas；And the opening (not shown) that spues,
Compressed gas is spued.
Axle 2 is that as rotary power the power produced by driver element 4 is transferred into compressor impeller 1a device, even
It is connected to driver element 4.
In addition, in a side of axle 2, being formed with mosaic process 2a, mosaic process 2a is embedded in compressor impeller 1a
Basal part 1c formation embedded hole 1e.In this wise, mosaic process 2a is chimeric with embedded hole 1e, thus, compressor impeller 1a and
Axle 2 is positioned in the radial direction, is adjusted to be located on same axle.
In addition, in mosaic process 2a, being formed with the moon that can be threadedly engaged positioned at the part of the another side of differential screw 3
Threaded portion (not shown).
Such axle 2 is formed by such as ferrous materials (for example, ferrous materials containing chromium and molybdenum).
Differential screw 3 is the device for fastening compressor impeller 1a and axle 2, and the differential screw 3 possesses：Impeller is threadedly engaged
Portion 3a, threadingly engages in the compressor impeller 1a for being located at one side；With axle thread junction surface 3b, threadingly engage in that to be located at its another
The axle 2 of one side.
In addition, in differential screw 3, being formed at the diameter of thread of impeller threaded connection 3a ridge and being formed at axle
The diameter of thread of threaded connection 3b ridge is identical, also, is formed at the convolution of impeller threaded connection 3a ridge
The convolution direction of ridge of the direction with being formed at axle thread junction surface 3b turns into same direction.
Moreover, in differential screw 3, the spacing for being formed at impeller threaded connection 3a ridge is formed as than being formed at
The spacing of axle thread junction surface 3b ridge is smaller.
So, impeller threaded connection 3a diameter of thread landform identical with the axle thread junction surface 3b diameter of thread is made
Into, thus the differential screw 3 is different from the differential screw of existing (patent document 4), it is not necessary that for mitigation in the diameter of thread
The purpose for the stress that different position is produced and the length for extending differential screw.Therefore, can compared with existing differential screw
Differential screw 3 is set to be formed as fully short.
Further, since the convolution direction of the ridge to be formed at impeller threaded connection 3a is engaged with being formed at axle thread
The convolution direction of portion 3b ridge is as same direction, thus as described later, using the differential screw 3 come by compressor leaf
When taking turns 1a and the fastening of axle 2, it is not necessary that compressor impeller 1a and axle 2 is relatively rotated, it becomes possible to fasten.
The spacing for being additionally, since the ridge for being formed at impeller threaded connection 3a is formed as than being formed at axle thread engagement
The spacing of portion 3b ridge is smaller, thus as described later, by the way that fixture is inserted into insertion from compressor impeller 1a front
Hole 1f and only rotate differential screw 3, thus, spacing official post compressor impeller 1a is moved in the way of approaching axle 2.Thus, most
Differential screw 3 and compressor impeller 1a can be fastened eventually.
Here, the convolution direction setting for being formed at axle thread junction surface 3b ridge is due to being produced when axle 2 rotates
Counter-force and the increased direction of fastening force of differential screw 3 and axle 2.Thus, even if the excessive torque due to such counter-force
Put between axle 2 and differential screw 3, the torque is not also acted on along the direction for unloading differential screw 3 from axle 2, but along will
The direction effect that differential screw 3 is screwed into towards axle 2.It is therefore prevented that the fastening force relaxation between axle 2 and compressor impeller 1a.
On the other hand, if excessive torque puts on pressure due to the counter-force produced when compressor impeller 1a rotates
Between contracting machine impeller 1a and differential screw 3, then the torque is acted on along the direction for unloading differential screw 3 from compressor impeller 1a.
But, as previously described, because the difference of impeller threaded connection 3a and axle thread junction surface 3b spacing, foregoing excessive torque is made
With so that compressor impeller 1a close to axle 2.It is therefore prevented that the fastening force relaxation between axle 2 and compressor impeller 1a.
In addition, in the differential screw 3 of present embodiment, impeller threaded connection 3a is along rotary shaft L direction ratio axle threads
Junction surface 3b is formed longerly.Because, as described later by differential screw 3 be installed on compressor impeller 1a and axle 2 it
Between when, it is necessary to initially impeller threaded connection 3a is threadingly engaged in compressor impeller 1a deeper.By making leaf in this wise
Wheel threaded connection 3a is longer than axle thread junction surface 3b, so as in advance be installed on differential screw 3 with stable state
Compressor impeller 1a.
In addition, in the differential screw 3 of present embodiment, impeller threaded connection 3a and axle thread junction surface 3b it
Between, provided with the non-screw division for not forming ridge.In addition, do not make impeller threaded connection 3a be formed, with differential screw 3 longlyer
Installation for the purpose of, in order that non-screw division is inserted into running through in through hole 1f, when manufacturing differential screw 3, it is necessary to
The diameter of non-screw division is set to be formed than the impeller threaded connection 3a smaller degree equivalent to the length of ridge of most external diameter.
But, compared with so additionally carrying out for making the less processing of the diameter of non-screw division, as long as being only threadedly engaged impeller
Portion 3a is formed longlyer, handling ease.Therefore, by making impeller threaded connection 3a longer than axle thread junction surface 3b
Formed, so as to suppress manufacturing cost.
In the end face (face of compressor impeller 1a sides) of differential screw 3, connecting hole 3c is formed with, connecting hole 3c can
Engage with the holding section (not shown) of fixture 10 for rotating differential screw 3.Connecting hole 3c, sees from rotary shaft L directions
See, be set as the shape (such as regular hexagon) using rotary shaft L as center of gravity.Thus, can be equal when compressor impeller 1a rotates
Etc. ground keep the distribution of weight centered on rotary shaft L in compressor impeller 1a, it is thus possible to make compressor impeller 1a stable
Ground rotates.In addition, the end face of differential screw 3 is by being formed as previously described in compressor impeller 1a basal part 1c insertion
Hole 1f and the outside for being exposed to through hole 1f.Therefore, the connecting hole 3c for being formed at the end face of differential screw 3 is also exposed to insertion
Hole 1f outside.
Further, since differential screw 3 is necessary to ensure that the rigidity required for the fastening of compressor impeller 1a and axle 2, thus
Preferably formed by the higher materials of thermal conductivity ratio compressor impeller 1a.
Specifically, in such as compressor impeller 1a by the case that titanium alloy is formed, preferably being formed by ferrous materials
Differential screw 3.
So, by forming differential screw 3 by the higher materials of thermal conductivity ratio compressor impeller 1a, so as to promote
Can rapidly it be carried out to by not shown towards the heat transfer of axle 2 from the compression by gas and the compressor impeller 1a of high temperature
Cooling body cooling lubricating oil heat transfer.
In addition, formed in differential screw 3 by ferrous materials and compressor impeller 1a is by the case that titanium alloy is formed, it is differential
Thermal expansion of the thermal expansion of screw 3 than compressor impeller 1a is bigger.Therefore, if the fastening part of compressor impeller 1a and axle 2 into
For high temperature, then exist and be particularly due to differential screw 3 than compressor impeller 1a larger thermal expansion and compressor impeller 1a and axle 2
The possibility of separation.But, if it is possible to as previously mentioned by based on the cooling that the heat transfer caused by differential screw 3 promotes
The temperature change of fastening part is suppressed smaller, then can reduce thermal expansion, it is thus possible to suppresses 2 points of compressor impeller 1a and axle
From.Therefore, it is possible to prevent such as compressor impeller 1a and differential screw 3 fastening force from relaxing.
In addition, in the present embodiment, differential screw 3 is threadedly engaged with compressor impeller 1a, differential screw 3 and the spiral shell of axle 2
Line is engaged, thus differential screw 3 and compressor impeller 1a contact area and differential screw 3 and the contact area expansion of axle 2.Cause
This, due to heat transfer area increase, thus further promotes foregoing heat transfer.
Driver element 4 is the device for producing the power for rotating compressor impeller 1a and being transferred to axle 2, for example, possessing electricity
Motivation or gear etc..
The nose shell 9 of the opening portion 1j occlusions of the through hole 1f front end face for being formed at compressor impeller 1a possessed into hemisphere
The cover body 9a and outer screw section 9b of shape.In cover body 9a, the engaging for being sticked in the fixture for rotating nose shell 9 is formed with
Portion (not shown).(do not scheme moreover, outer screw section 9b threadingly engages in the female threaded portion to be formed in through hole 1f opening portion 1j sides
Show), thus, cover body 9a coverings opening portion 1j.Thus, nose shell 9 is releasably installed on through hole 1f opening portion 1j, will
Opening portion 1j occlusions.In addition, in the installation of such nose shell 9, it is preferable that sun will be inserted in outside O-ring (not shown) in advance
Threaded portion 9b, makes foregoing O-ring around the 1j of opening portion between cover body 9a, and nose shell 9 and compressor are improved in advance
Air-tightness between impeller 1a.
Here, the convolution direction setting for being formed at the outer screw section 9b of nose shell 9 ridge is due in compressor leaf
Take turns the counter-force produced during 1a rotations and outer screw section 9b and compressor impeller the 1a increased direction of fastening force.Thus, though by
Counter-force when compressor impeller 1a rotates and excessive torque is put between nose shell 9 and compressor impeller 1a, the torque
Also do not acted on along the direction for unloading nose shell 9 from compressor impeller 1a, but along the direction that nose shell 9 is screwed into through hole 1f
Effect.It is therefore prevented that the fastening force relaxation between nose shell 9 and compressor impeller 1a.
In the turbo-compressor S1 of the present embodiment with such composition assembling, in order to by compressor impeller 1a
Fastened with axle 2, first, the part coupled in compressor impeller 1a through hole 1f with axle 2, by the impeller spiral shell of differential screw 3
Line junction surface 3a is threadedly engaged.Now, the impeller threaded connection 3a entirety formed longerly than axle thread junction surface 3b is made
It is screwed on through hole 1f receiving space.
Axle 2 is located at next, making somewhat to threadingly engage in from the through hole 1f axle thread junction surface 3b protruded leading section
Female threaded portion.
Next, as shown in Fig. 2 fixture 10 (six side spanners) insertion to be formed to compressor impeller 1a basal part 1c's
Through hole 1f, makes the holding section for being configured at the front end of fixture 10 be embedded in the connecting hole 3c exposed from through hole 1f.Then, pass through
Rotate fixture 10, so that differential screw 3 rotates.
As a result, do not make compressor impeller 1a in rotary moving towards axle 2, just can by the rectilinear movement along rotary shaft L
Make compressor impeller 1a close to axle 2.This is due to the convolution direction of impeller threaded connection 3a ridge is engaged with axle thread
The convolution direction of portion 3b ridge is same direction, moreover, the gap ratio axle thread of impeller threaded connection 3a ridge
The spacing of junction surface 3b ridge is smaller.Then, mosaic process 2a is embedded in embedded hole 1e, rotates differential screw 3, until
Untill compressor impeller 1a is close to axle 2, thus, compressor impeller 1a is fastened with axle 2.
In the turbo-compressor S1 of present embodiment, the spiral shell for the ridge for making to be formed at impeller threaded connection 3a is used
The diameter of thread identical differential screw 3 of ridge of the line diameter with being formed at axle thread junction surface 3b, by compressor impeller 1a
Fastened with axle 2.Therefore, it is not necessary to the stress produced as prior art for mitigation at the different position of the diameter of thread
Purpose and the length for extending differential screw 3.Therefore the increase of the workload due to pretension can, be suppressed.
In addition, in the turbo-compressor S1 of present embodiment, due to impeller threaded connection 3a and axle thread junction surface
The difference of 3b spacing and compressor impeller 1a is moved linearly towards axle 2, thus, eventually through differential screw 3 by compressor
Impeller 1a is fastened with axle 2.Therefore, do not produced in seated surface (end face of the axle contacted with impeller) along with compressor impeller 1a's
The frictional force of rotation, only utilizes the frictional force produced in the threaded face of formation, it becomes possible to be compressed machine impeller 1a and axle 2
Fastening.Therefore, it is possible to reduce the torque required for fastening, workload during reduction fastening.
In addition, in the turbo-compressor S1 of present embodiment, not applying as tensioning bolt to be used for the feelings of differential screw 3
The such big tension force of condition, it becomes possible to fasten compressor impeller 1a with axle 2.Therefore, do not need separately hydraulic tensioner etc. complicated and big
Device, it becomes possible to compressor impeller 1a is anchored on axle 2.
In addition, in the turbo-compressor S1 of present embodiment, the through hole 1f in the inside located at compressor impeller 1a
Inner wall part in due to apply highest stress and load become very big compressor impeller 1a maximum gauge part it is relative
The region (maximum stress portion) answered, is formed with negative thread.But, due to corresponding with closely spaced impeller threaded connection 3a,
The spacing of the negative thread is also small, thus is difficult to the stress of generation circumferencial direction, and durability is improved.
In addition, in the turbo-compressor S1 of present embodiment, due to making impeller threaded connection 3a ridge spacing
The spacing of ridge than axle thread junction surface 3b is smaller, thus in impeller threaded connection 3a between through hole 1f,
The mutual contact area of ridge becomes big.Therefore, easily from impeller maximum gauge portion (high maximum temperature portion) heat release of the highest temperature.
In addition, in the turbo-compressor S1 of present embodiment, due to making compressor leaf when differential screw 3 rotates one time
The conveying capacity for taking turns 1a is small, it is thus possible to reduce the torque required for movement.
In addition, in the turbo-compressor S1 of present embodiment, with impeller threaded connection 3a than axle thread junction surface 3b
Longer mode forms differential screw 3.Therefore, can when differential screw 3 is installed between compressor impeller 1a and axle 2
Initially impeller threaded connection 3a is set to threadingly engage in compressor impeller 1a deeper.Therefore, it is possible in advance by differential screw 3 with
Stable state is installed on compressor impeller 1a.
In addition, in the turbo-compressor S1 of present embodiment, in through hole 1f opening portion 1j releasably fitting machines
Head-shield 9, by opening portion 1j occlusions.Thus, because moisture or foreign matter do not enter in through hole 1f, it is thus possible to prevent moisture from causing
The getting rusty of differential screw 3, damage of differential screw 3 etc. caused by foreign matter.That is, it is being necessary differential screw when safeguarding etc.
3 from compressor impeller 1a and axle 2 dismounting in the case of, can prevent differential screw 3 from not falling off.Therefore, it is possible to improve differential spiral shell
The durability of nail 3, it is thus possible to less expensive material is for example used for differential screw 3.
In addition, in the turbo-compressor S1 of present embodiment, will be formed in time of axle thread junction surface 3b ridge
Rotation direction setting is the direction of the counter-force due to being produced when axle 2 rotates and the fastening force raising of differential screw 3 and axle 2.Therefore,
Even if due to such counter-force, excessive torque is put between axle 2 and differential screw 3, and the torque is not also along by differential screw
The 3 direction effects unloaded from axle 2, but acted on along the direction that differential screw 3 is screwed into axle 2.Therefore, it is possible to prevent axle 2 and pressure
Fastening force relaxation between contracting machine impeller 1a.
In addition, in the turbo-compressor S1 of present embodiment, the end face in the compressor impeller 1a sides of differential screw 3,
The connecting hole 3c that holding section provided with the fixture 10 for rotating differential screw 3 can engage, also, be provided with compressor impeller 1a
Make the through hole 1f that connecting hole 3c exposes.Therefore, by the way that fixture 10 is inserted into through hole 1f, so as to utilize the card of fixture 10
Conjunction portion engaging with connecting hole 3c easily rotates differential screw 3.
In addition, in the turbo-compressor S1 of present embodiment, by differential screw 3 by compressor impeller 1a and axle 2
Fastening.Therefore, it is not necessary to extend up to axle 2 as existing turbo-compressor in order to which compressor impeller 1a is fixed
Compressor impeller 1a front end.As a result, it is possible to shorten axle 2, it is possible to increase the rigidity of axle 2.
(the 2nd embodiment)
Then, the 2nd embodiment to the present invention is illustrated.In addition, in the explanation of the 2nd embodiment with it is foregoing
1st embodiment identical part, is omitted or simplified its explanation.
Fig. 3 A and Fig. 3 B are the figures of the schematic configuration for the turbo-compressor S2 for showing present embodiment, and Fig. 3 A are side cross-sectionals
Figure, Fig. 3 B are the front views that axle 2 is watched from rotary shaft L directions.
As shown in these Fig. 3 A and Fig. 3 B, the turbo-compressor S2 of present embodiment possesses pin member 5, and it is with rotary shaft L
Direction as length direction, be embedded in the position for the deviation rotary shaft L for being located at compressor impeller 1a embedded hole (not shown) and
It is located at the embedded hole (not shown) of the deviation rotary shaft L of axle 2 position.
Compressor impeller 1a is in rotary moving relative to axle 2 for suppressing for pin member 5, is used as the rotation of the present invention to suppress machine
Structure and work.
Moreover, in the turbo-compressor S2 of present embodiment, as shown in Figure 3 B, multiple (in the present embodiment, 4)
Pin member 5 is along the circumferential direction centered on compressor impeller 1a rotary shaft L to configure at equal intervals.In addition, multiple pin members 5
As long as quantity is set to follow above-mentioned configuration condition, it is not necessary that be defined in 4.
According to the turbo-compressor S2 with such present embodiment constituted, compressor impeller 1a is being installed on axle
When 2, compressor impeller 1a can be suppressed by pin member 5 and rotated relative to axle.Therefore, it is possible to non-rotary stable shape
State fastens compressor impeller 1a with axle 2.
Further, since pin member 5 can be made to be acted as compressor impeller 1a with the reinforcement at the junction of axle 2
With, it is thus possible to improve compressor impeller 1a and the intensity of the junction of axle 2.
In addition, the turbo-compressor S2 according to present embodiment, when compressor impeller 1a and axle 2 are fastened, makes in advance
Pin member 5 is embedded in a side of compressor impeller 1a and axle 2, approaches compressor impeller 1a by the rotation of differential screw 3
Axle 2 is simultaneously embedded in the opposing party.
Therefore, compressor impeller 1a is in rotary moving relative to axle 2 to be showed making when compressor impeller 1a is fastened with axle 2
In some fastening methods, it is impossible to configure pin member 5.
That is, the turbo-compressor S2 of present embodiment, which can be realized, makes the strong of compressor impeller 1a and the junction of axle 2
Spend the effect improved.On the other hand, using make compressor impeller 1a relative to axle 2 existing fastening method in rotary moving
In turbo-compressor, it is impossible to realize such effect.
In addition, in the turbo-compressor S2 of present embodiment, by multiple pin members 5 along with compressor impeller 1a rotation
Circumferential direction centered on axle L is equally spaced configured.Therefore, when compressor impeller 1a rotates, it can equably keep rotating
The distribution of weight along direction of rotation in compressor impeller 1a centered on axle L.Therefore, it is possible to make compressor impeller 1a stable
Ground rotates.
(the 3rd embodiment)
Then, the 3rd embodiment to the present invention is illustrated.In addition, in the explanation of the 3rd embodiment, on
Foregoing 1st embodiment identical part, is also omitted or simplified its explanation.
Fig. 4 A and Fig. 4 B are the figures of the schematic configuration for the turbo-compressor S3 for showing present embodiment, and Fig. 4 A are side cross-sectionals
Figure, Fig. 4 B are the front views that axle 2 is watched from rotary shaft L directions.
As shown in these Fig. 4 A and Fig. 4 B, the turbo-compressor S3 of present embodiment, from compressor impeller 1a rotary shaft L
The shape of direction viewing is the general triangular (shape deviateed from circle) in circle on each summit, also, is possessed with rotary shaft L
The embedded hole 6 being fitted together to by the mosaic process 7 and the mosaic process 7 of center of gravity.
Such mosaic process 7 and embedded hole 6 are suppressed rotations of the compressor impeller 1a relative to axle 2 by chimeric and moved
It is dynamic, worked as the rotation restraint mechanism of the present invention.
In addition, in the turbo-compressor S3 of present embodiment, mosaic process 7 is located at axle 2, embedded hole 6 is located at compressor
Impeller 1a.
Mosaic process 7 is located at compressor impeller 1a and embedded hole 6 is located at axle 2 however, it is also possible to use on the contrary
Constitute.
Foundation has the turbo-compressor S3 of such present embodiment constituted, by mosaic process 7 and can be fitted together to
Hole 6 and suppress when axle 2 is installed on into compressor impeller 1a compressor impeller 1a rotate.Therefore, it is possible to non-rotary stabilization
State fastens compressor impeller 1a and axle 2.
In addition, in the turbo-compressor S3 of present embodiment, mosaic process 7 has the shape using rotary shaft L as center of gravity.
Therefore, when compressor impeller 1a rotates, can equably keep in the compressor impeller 1a centered on rotary shaft L along
The distribution of weight of direction of rotation.Therefore, it is possible to be stably rotated compressor impeller 1a.
More than, referring to the drawings and embodiments of the present invention are illustrated, but the present invention is not limited to such reality
Apply mode.All Multiple Shapes of each component parts shown in foregoing embodiment or combination etc. are an examples, are not being taken off
In the range of purport from the present invention, various changes can be carried out based on design requirement etc..
For example, in embodiments of the present invention, mosaic process 2a is located at axle 2, embedded hole 1e is located at compressor impeller 1a.
But, as shown in figure 5, also mosaic process can be located at into compressor impeller 1a on the contrary and embedded hole is located at into axle
2。
In this case, as shown in figure 5, differential screw 3 enters the deeper position of the inside of axle 2 and configured.Accordingly, it is capable to
Enough make differential screw 3 from the stress due to applying maximum in the through hole 1f for the inside for being located at compressor impeller 1a internal face
And load becomes the very big region (maximum stress portion) corresponding with compressor impeller 1a maximum gauge part and kept out of the way.Cause
This, can make the load reduction for acting on differential screw 3.In addition, by making differential screw 3 deviate compressor impeller 1a maximum
Stress portion, so as to which higher axle power is additional into compressor impeller 1a, can make compressor impeller 1a and axle 2 fastening force
Increase.
In addition, in embodiments of the present invention, prevent for the rotation being compressed between machine impeller 1a and axle 2 and its
Positioning, employs the composition or pin member using mosaic process and embedded hole, but it is also possible to instead of these parts using for example
Fluted disc (curvic coupling).
In addition, in embodiments of the present invention, in order to suppress the relaxation of the fastening force caused by thermal expansion in operation,
The axle power for the relaxation that can relax the fastening force caused by thermal expansion can also be assigned to differential screw 3 in advance.
In addition, in embodiments of the present invention, as shown in Fig. 2 differential screw 3 possesses the connecting hole for engaging fixture 10
3c。
However, the present invention does not limit this, the engaging that the holding section of fixture can also be set in differential screw 3 can engage is dashed forward
Rise, to replace connecting hole 3c.
In addition, in embodiments of the present invention, a compressor impeller is fastened with to an axle and in one end of the axle
1a turbo-compressor is illustrated.
However, the present invention is not limited to this.For example, can also be applied to each be fastened with compressor at the two ends of an axle
Impeller 1a turbo-compressor, possess multiple axles and each axle provided with compressor impeller turbo-compressor, be provided additionally with cooling
The turbo-compressor of the other equipments such as the cooler of compressed gas.
Industrial applicability
According to the turbomachinery of the present invention, especially the screw thread using the ridge for making to be formed at impeller threaded connection is straight
The diameter of thread identical differential screw of ridge of the footpath with being formed at axle thread junction surface, impeller and axle are fastened.Therefore, do not have
Be necessary as in the past like that in order to relax extend the length of differential screw in the stress of the different position generation of the diameter of thread.Cause
This, can suppress the increase of the workload due to pretension.
Symbol description
S1 ~ S3 turbo-compressor (turbomachinery)
1 compressor
1a compressor impellers (impeller)
1b compressor housings
1c basal parts
1d blades
1e embedded holes
1f through holes
1g suction openings
1h diffusers
1i scroll streams
1j opening portions
2 axles
2a mosaic processes
3 differential screws
3a impeller threaded connections
3b axle threads junction surface
3c connecting holes
4 driver elements
5 pin members (rotation restraint mechanism)
6 embedded holes (rotation restraint mechanism)
7 mosaic processes (rotation restraint mechanism)
9 nose shells (lid)
10 fixtures.
Claims (13)
1. a kind of turbomachinery, is the turbomachinery for the axle for possessing the impeller of rotation and rotary power being transferred to the impeller,
Possesses differential screw, the differential screw, which has to be located at a side and threadingly engage in the impeller of the impeller, to be threadedly engaged
Portion and it is located at another side and threadingly engages in the axle thread junction surface of the axle, the impeller and the axle is fastened,
The differential screw is formed as：
It is formed at the diameter of thread of the ridge of the impeller threaded connection and is formed at the screw thread at the axle thread junction surface
The diameter of thread of tooth is identical,
It is formed at the convolution direction of the ridge of the impeller threaded connection and is formed at the screw thread at the axle thread junction surface
The convolution direction of tooth is same direction, moreover,
The gap ratio for being formed at the ridge of the impeller threaded connection is formed at the ridge at the axle thread junction surface
Spacing is smaller.
2. turbomachinery according to claim 1, it is characterised in that the impeller threaded connection connects than the axle thread
Conjunction portion is longer.
3. turbomachinery according to claim 1, it is characterised in that
The impeller possesses the insertion being threadedly engaged with the impeller threaded connection of the differential screw along its rotary shaft
Hole,
In the opening portion of the remote axle of the through hole, releasably provided with by the lid of the opening port blocking.
4. turbomachinery according to claim 1, it is characterised in that differential screw impeller as described in thermal conductivity ratio
Higher material is formed.
5. turbomachinery according to claim 4, it is characterised in that the impeller is formed by titanium alloy, the differential spiral shell
Nail is formed by ferrous materials.
6. turbomachinery according to claim 1, it is characterised in that possess and suppress rotation of the impeller relative to the axle
The dynamic rotation restraint mechanism of transfer.
7. turbomachinery according to claim 6, it is characterised in that
The rotation restraint mechanism is pin member, and it is embedded in and be located at using the rotation direction of principal axis of the impeller as length direction
The embedded hole of the position of the deviation rotary shaft of the impeller and be located at the axle deviation rotary shaft position embedded hole.
8. turbomachinery according to claim 7, it is characterised in that multiple pin members are with the rotation of the impeller
Equally spaced configured in circumferential direction centered on axle.
9. turbomachinery according to claim 6, it is characterised in that
The rotation restraint mechanism possesses：
Mosaic process, the outer shape from the rotation direction of principal axis viewing of the impeller is the shape from round-shaped deviation, also,
Protrude and set along the rotation direction of principal axis in a side of the impeller and the axle；With
Embedded hole, is located at the opposing party of the impeller and the axle, also, the mosaic process is fitted together to.
10. turbomachinery according to claim 9, it is characterised in that there is center of gravity to be located at rotary shaft for the mosaic process
On shape.
11. turbomachinery according to claim 1, it is characterised in that be formed at the ridge at the axle thread junction surface
Convolution direction setting be that the fastening force of the differential screw and the axle due to the counter-force that is produced when the axle rotates is carried
High direction.
12. turbomachinery according to claim 1, it is characterised in that
In the end face of the impeller side of the differential screw, provided with the holding section for being sticked in the fixture for rotating the differential screw
Connecting hole or engaging protrusion,
In the impeller, provided with the through hole for exposing the connecting hole or engaging protrusion.
13. turbomachinery according to claim 12, it is characterised in that being sticked in makes the fixture of the differential screw rotation
Holding section the connecting hole or engaging protrusion have center of gravity be located at the impeller rotary shaft on shape.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2012-131785 | 2012-06-11 | ||
| JP2012131785 | 2012-06-11 | ||
| PCT/JP2013/066065 WO2013187403A1 (en) | 2012-06-11 | 2013-06-11 | Turbo machine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104350284A CN104350284A (en) | 2015-02-11 |
| CN104350284B true CN104350284B (en) | 2017-08-08 |
Family
ID=49758225
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201380030055.0A Active CN104350284B (en) | 2012-06-11 | 2013-06-11 | Turbomachinery |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US9624942B2 (en) |
| EP (1) | EP2860402B1 (en) |
| JP (1) | JP5880706B2 (en) |
| KR (1) | KR101681661B1 (en) |
| CN (1) | CN104350284B (en) |
| WO (1) | WO2013187403A1 (en) |
Families Citing this family (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5589889B2 (en) * | 2011-02-21 | 2014-09-17 | 株式会社Ｉｈｉ | Turbo machine |
| JP5967966B2 (en) * | 2012-02-13 | 2016-08-10 | 三菱重工コンプレッサ株式会社 | Impeller and rotating machine equipped with the same |
| GB201314270D0 (en) | 2013-08-09 | 2013-09-25 | Aeristech Ltd | Aerodynamic enhancements in compressors |
| DE102013015563A1 (en) * | 2013-09-20 | 2015-03-26 | Abb Turbo Systems Ag | turbocharger |
| US9835164B2 (en) * | 2014-10-03 | 2017-12-05 | Electro-Motive Diesel, Inc. | Compressor impeller assembly for a turbocharger |
| JP6631094B2 (en) * | 2015-08-26 | 2020-01-15 | 株式会社Ihi | Rotating machinery |
| CN105604979B (en) * | 2015-12-21 | 2018-09-07 | 重庆美的通用制冷设备有限公司 | Stage impeller component and centrifugal compressor with it |
| CN109312661B (en) * | 2016-09-02 | 2020-12-25 | 株式会社Ihi | Impeller for supercharger |
| JP2018114565A (en) * | 2017-01-16 | 2018-07-26 | 三菱マテリアル株式会社 | Cutting tool |
| US10677261B2 (en) * | 2017-04-13 | 2020-06-09 | General Electric Company | Turbine engine and containment assembly for use in a turbine engine |
| DE112019002640B4 (en) * | 2018-05-24 | 2023-01-05 | Ihi Corporation | rotating body and turbocharger |
| US10914231B2 (en) * | 2018-08-21 | 2021-02-09 | Ryan Harold SALENBIEN | Hub-less and nut-less turbine wheel and compressor wheel design for turbochargers |
| US11598294B2 (en) | 2018-08-21 | 2023-03-07 | Apexturbo Llc | Hub-less and nut-less turbine wheel and compressor wheel designs and installation/removal tool |
| WO2024010582A1 (en) * | 2022-07-07 | 2024-01-11 | Siemens Energy Global GmbH & Co. KG | Coupling joints to interconnect and transmit rotational torque between adjacent impeller bodies in a turbomachine |
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2013
- 2013-06-11 JP JP2014521345A patent/JP5880706B2/en active Active
- 2013-06-11 CN CN201380030055.0A patent/CN104350284B/en active Active
- 2013-06-11 KR KR1020147028038A patent/KR101681661B1/en active Active
- 2013-06-11 EP EP13804192.6A patent/EP2860402B1/en active Active
- 2013-06-11 WO PCT/JP2013/066065 patent/WO2013187403A1/en active Application Filing
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| GB340450A (en) * | 1930-03-07 | 1931-01-01 | Napier & Son Ltd | Improvements in or relating to rotors |
| JP2002310121A (en) * | 2001-04-13 | 2002-10-23 | Misawa Homes Co Ltd | Set machine screw |
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Also Published As
| Publication number | Publication date |
|---|---|
| EP2860402A4 (en) | 2016-02-24 |
| KR20140143170A (en) | 2014-12-15 |
| US9624942B2 (en) | 2017-04-18 |
| EP2860402B1 (en) | 2019-10-02 |
| JP5880706B2 (en) | 2016-03-09 |
| WO2013187403A1 (en) | 2013-12-19 |
| US20150093247A1 (en) | 2015-04-02 |
| KR101681661B1 (en) | 2016-12-01 |
| JPWO2013187403A1 (en) | 2016-02-04 |
| CN104350284A (en) | 2015-02-11 |
| EP2860402A1 (en) | 2015-04-15 |
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